CN209621972U - Few teeth difference involute deceleration mechanism - Google Patents
Few teeth difference involute deceleration mechanism Download PDFInfo
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- CN209621972U CN209621972U CN201821694446.9U CN201821694446U CN209621972U CN 209621972 U CN209621972 U CN 209621972U CN 201821694446 U CN201821694446 U CN 201821694446U CN 209621972 U CN209621972 U CN 209621972U
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- gear
- shaft
- planet carrier
- input shaft
- planetary
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- 230000007246 mechanism Effects 0.000 title claims abstract description 38
- 239000004744 fabric Substances 0.000 claims 1
- 238000010008 shearing Methods 0.000 abstract description 7
- 239000000969 carrier Substances 0.000 abstract 1
- 230000005540 biological transmission Effects 0.000 description 11
- 238000010586 diagram Methods 0.000 description 8
- 230000033001 locomotion Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 238000003754 machining Methods 0.000 description 2
- 239000007787 solid Substances 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000003967 crop rotation Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002787 reinforcement Effects 0.000 description 1
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Abstract
The input shaft of few teeth difference involute deceleration mechanism is one and sets cogged d-axis, and the center of planetary gear mechanism is arranged in the shaft of input shaft；Planetary gear mechanism include ring gear, quantity it is equal and at least two the first planetary gear and eccentric shaft, first planet carrier, two the second fewer differential teeth planetary wheels and the second planet carriers；Ring gear is immobilized in the shell；First planetary gear is evenly arranged on the gear of input shaft；Eccentric shaft is fixed on the center of the first planetary gear, and sequentially passes through first planet carrier, the second fewer differential teeth planetary wheel and the second planet carrier；Second fewer differential teeth planetary wheel is engaged with ring gear, and first planet carrier and the second planet carrier are connect by bearing with ring gear；Ring gear is fixed inside the shell；Output shaft is fixedly connected with the second planet carrier, and output shaft is overlapped with the axis of input shaft.Power is averagely diverted on each eccentric shaft, this structure of counterweight is eliminated.Dynamic branch also reduces the shearing force that eccentric shaft is undertaken, and improves service life.
Description
Technical field
The utility model belongs to a kind of retarder, specially a kind of few teeth difference involute deceleration mechanism.
Background technique
Planet-gear transmission is one of Planetary Gear Transmission, by external gear and internal gear partner in nibble
Gear pair is closed, it is 1~5 using involute profile, the teeth number difference very little of internal-external gear, usual teeth number difference, and external tooth passes through
Bearing and eccentric bushing are mounted on the input shaft of retarder, and internal gear is mostly fixed.Output mechanism is by the rotation of external gear
It is passed on output shaft by pin shaft, and guarantees that its angular speed is constant.
Planet-gear transmission is broadly divided into two kinds of N-type (K-H-V type), NN type (2K-H type) structures.
In N-type transmission, eccentric shaft is power input shaft, needs to bear very big shearing force.In the rotation of eccentric shaft
And under the limitation of internal gear, it is flat that planet crop rotation plane motion, i.e. planetary gear had both made circumference around the axis that internal gear position is fixed
Shifting movement also makees rotary motion around own axes.Since the axial location of output shaft is fixed, it is therefore necessary to by defeated
The rotary motion of planetary gear could be passed to output shaft by mechanism out.Currently, output mechanism mainly uses cross slider type, floats
Disc type and pin hole formula.And in these three output mechanisms, on planetary gear and planet carrier, required pin hole quantity is more, accordingly for
The requirement on machining accuracy of pin hole is high, is not easy to produce and process.In addition, pin shaft, guide, being sliding friction between external tooth three, pass
Efficiency of movement and carry property influenced by part processing precision.Due in gear rotation process, the guide on pin shaft is with pin hole
Localized contact, so guide is easy to wear, the service life is short.
And NN type transmission in, although theoretic gear range is wider, it is practical in when transmission ratio is very big, transmission
Efficiency is very low, so transmission ratio should not be too large when needing to consider transmission efficiency.Simultaneously in rotation, inevitably
Generate vibration.For strict guarantee dynamic balancing, need to increase counterweight to guarantee mechanism smooth running.And increase this design of counterweight
It is only applicable to large gear.And miniature gear is limited by space, then can not increase counterweight.
It can be seen from the above, existing small teeth number difference planet gear there are the problem of have: 1, need to increase counterweight, can be in gear
Eccentric shaft is avoided to generate biggish vibration when rotation, to guarantee stability of rotation.And increase counterweight and is only applicable to large gear, it is small
Type gear is not available.2, eccentric shaft is power input shaft, undertakes biggish shearing force, easy to damage.3, planetary gear and planet carrier
On need to process multiple pin holes and connect with output mechanism.Pin hole is more, and the requirement to machining accuracy is higher.4, it was rotated in gear
Cheng Zhong is localized contact between the guide and pin hole on pin shaft, and guide is easy to wear, the service life is short.
Utility model content
In view of this, the present invention provides a kind of few teeth difference involute deceleration mechanisms, cancel original counter weight construction, make
Gear still is able to smooth rotation；Meanwhile the shearing force that eccentric shaft is undertaken is reduced, improve the service life of eccentric shaft.
The technical solution of the utility model is a kind of few teeth difference involute deceleration mechanism, including input shaft, output shaft and
Positioned at the intracorporal planetary gear mechanism of shell；It is characterized by: the input shaft is a d-axis, axis of the input shaft close to input terminal
Bar is equipped with gear, and the center of planetary gear mechanism is arranged in the shaft of input shaft；The planetary gear mechanism includes interior
Gear ring, the first planetary gear, first planet carrier, the second fewer differential teeth planetary wheel, the second planet carrier and eccentric shaft；The ring gear is solid
It is scheduled in shell；The second fewer differential teeth planetary wheel is two；First planetary gear is identical with the quantity of eccentric shaft and at least
It is two；First planetary gear is evenly arranged on the circumference of input shaft gear and engages；In the centre bit of the first planetary gear
It sets and is respectively and fixedly provided with an eccentric shaft, eccentric shaft sequentially passes through on first planet carrier, the second fewer differential teeth planetary wheel and the second planet carrier
The through-hole of corresponding setting, eccentric shaft are connect by bearing with through-hole；The second fewer differential teeth planetary wheel is nibbled with the ring gear
It closes, the first planet carrier and the second planet carrier are connect by bearing with ring gear；The ring gear is fixed in the shell；
The output shaft is fixedly connected with the second planet carrier, and the axis of output shaft is overlapped with the axis of input shaft.
Further, the phase phase difference of the second fewer differential teeth planetary wheel is 180 °.
Further, the quantity of first planetary gear and eccentric shaft is three or four.
Further, the input terminal of the input shaft is a bevel gear wheel, and bevel gear wheel is engaged with a bevel pinion, small
Bevel gear connect with external power mechanism.
Further, the bevel gear wheel engagement range of the bevel pinion and input shaft is at 10 ° ~ 170 °.
Further, the input shaft is roller gear close to the gear of input terminal.
Further, the input shaft passes through the centre bore of the second fewer differential teeth planetary wheel, and the aperture of the centre bore is greater than input
The diameter of axle of axis.
Further, it is connected between the eccentric shaft and the second fewer differential teeth planetary wheel by needle bearing.
Further, the first planet carrier is equipped at least two reinforcers, reinforcer point on the symmetrical position of central point
Not between the through-hole of the first planet carrier；The identical reinforcer of quantity is provided on the second fewer differential teeth planetary wheel to pass through
Perforation, reinforcer can be inserted into reinforcer through hole.
Further, the axis pin hole parallel with input shaft axis is offered on the reinforcer, on second planet carrier
Pin hole is equally offered, reinforcer perforation opposite with the pin hole on the second planet carrier is simultaneously connected by pin shaft.
The beneficial effects of the utility model are, by the first planetary gear engaged with input shaft, the power of input is put down
Be diverted on each eccentric shaft, avoided the need for from structure increase counterweight can smooth rotation the problem of.It is same with this
When, dynamic branch also reduces the shearing force that eccentric shaft is undertaken, and improves the service life of eccentric shaft.
Detailed description of the invention
Fig. 1 is the structural schematic diagram of the utility model.
Fig. 2 is the transmission principle figure of the utility model.
Fig. 3 is the structural schematic diagram of the first planetary gear.
Fig. 4 is the structural schematic diagram that two the first planetary gears are engaged with input shaft.
Fig. 5 is the scheme of installation of two the first planetary gears in the present invention.
Fig. 6 is the structural schematic diagram of the second fewer differential teeth planetary wheel.
Fig. 7 is the scheme of installation of the second fewer differential teeth planetary wheel in the present invention.
Fig. 8 is the structural schematic diagram of eccentric shaft.
Fig. 9 is the structural schematic diagram of input shaft.
Figure 10 is the structural schematic diagram of first planet carrier.
Figure 11 is the structural schematic diagram that three the first planetary gears are engaged with input shaft.
Figure 12 is the scheme of installation of three the first planetary gears in the present invention.
In figure: 1, output shaft, the 2, second planet carrier, 3, angular contact bearing, 4, ring gear, the 5, second fewer differential teeth planetary wheel,
6, needle bearing, 7, first planet carrier, 8, shell, the 9, first planetary gear, 10, eccentric shaft, 11, bevel gear wheel, 12, small bevel gear
Wheel, 13, input shaft, 14, deep groove ball bearing, 15, roller gear, 16, spline tooth, 17, centre bore, 18, through-hole, 19, reinforcer
Through hole, 20, reinforcer, 21, pin hole, 22, eccentric shaft, 23, spline.
Specific embodiment
In order to make those skilled in the art more fully understand the technical solution of the utility model, with reference to the accompanying drawing and have
The utility model is described in further detail for body embodiment.
A kind of few teeth difference involute deceleration mechanism, including input shaft 13, output shaft 1, planetary gear mechanism and shell 8.
As shown in Figure 1, planetary gear mechanism include the first planetary gear 9, first planet carrier 7, eccentric shaft 10, the second fewer differential teeth planetary wheel 5,
Second planet carrier 2 and ring gear 4.Wherein, the second fewer differential teeth planetary wheel 5 is two.The number of first planetary gear 9 and eccentric shaft 10
It measures identical and at least two.
It is below two citings with 10 numbers of the first planetary gear 9 and eccentric shaft, the structure of the utility model is carried out detailed
Describe in detail it is bright, it is specific as follows:
As shown in Figure 1, input shaft 13 is a d-axis.Input shaft 13 is engaged with two the first planetary gears 9, and is successively worn
Cross the center of 7, two the second fewer differential teeth planetary wheels 5 and the second planet carrier 2 of first planet carrier.Two the second fewer differential teeth planetaries
Wheel 5 is engaged in ring gear 4.First planet carrier 7 and the second planet carrier 2 are located at the two sides of two the second fewer differential teeth planetary wheels 5, and
It is connect respectively by bearing with ring gear 4.Ring gear 4 is fixedly connected with shell 8.Output shaft 1 and the fixed company of the second planet carrier 2
It connects, the axis of output shaft 1 is overlapped with the axis of input shaft 13.
As shown in Fig. 1 and Fig. 9, the input terminal of input shaft 13 is a bevel gear wheel 11, the bevel gear wheel 11 of input shaft 13
It is engaged with a bevel pinion 12.Bevel pinion 12 is connect with external power mechanism, defeated for passing to external power
Enter axis 13.Engagement range between the bevel gear wheel 11 and bevel pinion 12 of input shaft 13 is 10 ° ~ 170 °.
As shown in Fig. 1 and Fig. 9, it is by input terminal shaft that input shaft 13 is engaged with two the first planetary gears 9
What gear was realized, which is roller gear 15.As shown in figure 4, two the first planetary gears 9 are evenly arranged on the circumference of roller gear 15
On, and engaged with roller gear 15.Sun gear of the roller gear 15 as two the first planetary gears 9.Input shaft 13 is worn simultaneously
Cross the centre bore 17 of two the second fewer differential teeth planetary wheels 5.The diameter of axle of input shaft 13 is less than centre bore 17 at centre bore 17
Aperture.Input shaft 13 is connect by bearing with first planet carrier 7 and the second planet carrier 2.Deep groove ball bearing 14 can be selected in the bearing.
Retaining ring is equipped on input shaft 13 by bearing, for limiting the axial displacement of input shaft 13.
In the present invention, the effect of the first planetary gear 9 is dynamic branch.When input shaft 13 obtains power input rotation
Afterwards, power can be averagely allocated to two the first planetary gears 9 by the roller gear 15 on input shaft 13.Two the first planetary gears 9 are again
By respective eccentric shaft 10, two the second fewer differential teeth planetary wheels 5 are imparted power to jointly.Specific drive mechanism is as follows:
Such as Fig. 1, Fig. 3 to Fig. 5, two the first planetary gears 9 are rotated under the drive of input shaft 13.Two the first planets
The structure of wheel 9 is identical.An eccentric shaft 10 is respectively fixed in the center of the first planetary gear 9.Two eccentric shafts 10
Structure it is identical.Eccentric shaft 10 and the fixed structure of the first planetary gear 9 can be used: open in 9 center of the first planetary gear
If a spline tooth 16, as shown in Figure 3.Corresponding spline 23 is installed with the fixed bit of the first planetary gear 9 in eccentric shaft 10, such as
Shown in Fig. 8.The spline 23 of eccentric shaft 10 is engaged on the spline tooth 16 at 9 center of the first planetary gear, eccentric shaft 10 is guaranteed with this
It is rotated synchronously with the first planetary gear 9.It is provided with retaining ring on the eccentric shaft 10 of 16 two sides of spline tooth, the first planetary gear is limited with this
9 axial displacement on eccentric shaft 10.
As shown in Fig. 1, Fig. 6 and Fig. 7, two the second fewer differential teeth planetary wheels 5 are engaged in ring gear 4.Two second few teeth
The two sides of poor planetary gear 5 are respectively first planet carrier 7 and the second planet carrier 2.First planet carrier 7 and the second planet carrier 2 respectively with
Ring gear 4 is connected by bearing.The bearing is angular contact bearing 3.As illustrated in figures 1 and 8, eccentric shaft 10 have two sections it is eccentric
Shaft 22, eccentric 22 quantity of shaft are consistent with the number of the second fewer differential teeth planetary wheel 5.Eccentric shaft 10 sequentially passes through the first planet
7, two the second fewer differential teeth planetary wheels 5 of frame and the second planet carrier 2.Wherein, two the second fewer differential teeth planetary wheels 5 are successively sleeved on
On 10 two sections of eccentric shaft eccentric shafts 22.It is connected between second fewer differential teeth planetary wheel 5 and eccentric shaft 10 by needle bearing 6.
It is connected respectively by deep groove ball bearing 14 between eccentric shaft 10 and first planet carrier 7 and the second planet carrier 2.Deep groove ball bearing 14 can
To replace with tapered roller bearing.Eccentric shaft 10 is equipped with gear at the position close to 2 bearing of first planet carrier 7 and the second planet carrier
Circle, for limiting the axial displacement of first planet carrier 7 and the second planet carrier 2 on eccentric shaft 10.
As shown in fig. 6, two the second fewer differential teeth planetary wheels 5 are equipped with the centre bore 17 penetrated for input shaft 13.
The symmetric position of two fewer differential teeth planetary wheels, 5 central point is equipped with the through-hole 18 for being set with eccentric shaft 10.The number of through-hole 18 and the
One planetary gear 9 is identical with the number of eccentric shaft 10.18 size of through-hole on second fewer differential teeth planetary wheel 5 is identical, position is opposite.When
When the through-hole 18 of former and later two the second fewer differential teeth planetary wheels 5 is overlapped, the external tooth of two the second fewer differential teeth planetary wheels 5 will appear mistake
Position.The phase difference of former and later two the second fewer differential teeth planetary wheels 5 is 180 °.When 10 rotational angle of eccentric shaft is 0 °, two second
Fewer differential teeth planetary wheel 5 and the meshing state of ring gear 4 are that one is engaged on the top of ring gear 4, and one is engaged on ring gear
4 bottom；When 10 rotational angle of eccentric shaft is 180 °, the meshing state of two second fewer differential teeth planetary wheels 5 and ring gear 4
It exchanges, one is engaged on the bottom of ring gear 4, and one is engaged on the top of ring gear 4.
The working principle of the utility model is as shown in Figure 2: bevel gear wheel 11 of the bevel pinion 12 with driven input shaft 13 rotates,
Two the first planetary gears 9 engaged with input shaft 13 are driven to rotate in turn.In the eccentric shaft 10 being fixedly connected with the first planetary gear 9
Under driving, two the second fewer differential teeth planetary wheels 5 engaged with ring gear 4 around 13 axis of input shaft while being revolved, also
Rotation can be carried out around the axis of itself.Again because the rotation of two the second fewer differential teeth planetary wheels 5, has driven two eccentric shafts
10 revolve around the axis of input shaft 13, that is, two the first planetary gears 9 revolve around the axis of input shaft 13.Due to
Two eccentric shafts 10 are connect by bearing with first planet carrier 7 and the second planet carrier 2, so two eccentric shafts 10 are around input shaft 13
The revolution of axis has driven first planet carrier 7 and the second planet carrier 2 around the rotation of 13 axis of input shaft.It is solid with the second planet carrier 2
Surely the output shaft 1 connected realizes its rotation vector finally under the drive of the second planet carrier 2 with the speed ratio of 1:1 by output shaft
1 transmitting outward.Since 11 engagement range of bevel gear wheel of bevel pinion 12 and input shaft 13 is at 10 ° ~ 170 °, so this is practical new
The input terminal and output end of type can be driven in the range of 10 ° ~ 170 °.
In the present invention, due to revolution that the rotation of first planet carrier 7 and the second planet carrier 2 is by eccentric shaft 10
Realization is pushed, in order to share the shearing force that first planet carrier 7 and the second planet carrier 2 are applied in revolution of eccentric shaft 10, into
And reinforce the transmission intensity of entire planetary gear mechanism, therefore in first planet carrier 7, the second fewer differential teeth planetary wheel 5 and the second row
Corresponding reinforcement structure is additionally arranged in carrier 2, specifically as shown in Fig. 6, Fig. 7 and Figure 10:
Reinforcer 20 there are two being set on the symmetrical position of 7 central point of first planet carrier.Two reinforcers 20 are located at
Between two neighboring through-hole 18.There are two reinforcer through holes 19 for setting on the second fewer differential teeth planetary wheel 5.Two reinforcers 20
It can be inserted into reinforcer through hole 19.To realize increase intensity, the purpose of shearing force is undertaken.In addition, on reinforcer 20
It is also provided with the axis pin hole 21 parallel with 13 axis of input shaft.Pin hole 21 is equally offered on second planet carrier 2.Reinforcer 20
Simultaneously pin shaft is connect for perforation opposite with the pin hole 21 on the second planet carrier 2.21 one side of pin hole plays the role of positioning, on the other hand
Torque can also be transmitted by pin shaft, carry torque.
As is illustrated by figs. 11 and 12, in the present invention, the first planetary gear 9 may be alternatively provided as three, and eccentric shaft 10 is
Three.As long as meeting three the first planetary gears 9 can be evenly arranged on the circumference of roller gear 15, and engage.Equally
, the first planetary gear 9 may be alternatively provided as four, and eccentric shaft 10 is four.
Claims (10)
1. a kind of few teeth difference involute deceleration mechanism, including input shaft, output shaft and it is located at the intracorporal planetary gear mechanism of shell；
It is characterized by: the input shaft is a d-axis, input shaft is equipped with gear, the shaft of input shaft close to the shaft of input terminal
The center of planetary gear mechanism is set；The planetary gear mechanism includes ring gear, the first planetary gear, the first planet
Frame, the second fewer differential teeth planetary wheel, the second planet carrier and eccentric shaft；The ring gear is immobilized in the shell；Described second few tooth
Poor planetary gear is two；First planetary gear is identical with the quantity of eccentric shaft and at least two；First planetary gear is equal
Cloth is on the circumference of input shaft gear and engages；It is respectively and fixedly provided with an eccentric shaft in the center of the first planetary gear, partially
Mandrel sequentially pass through first planet carrier, on the second fewer differential teeth planetary wheel and the second planet carrier corresponding setting through-hole, eccentric shaft
It is connect by bearing with through-hole；The second fewer differential teeth planetary wheel is engaged with the ring gear, the first planet carrier and second
Planet carrier is connect by bearing with ring gear；The ring gear is fixed in the shell；The output shaft and the second planet carrier
It is fixedly connected, the axis of output shaft is overlapped with the axis of input shaft.
2. few teeth difference involute deceleration mechanism as described in claim 1, it is characterised in that: the second fewer differential teeth planetary wheel
Phase phase difference is 180 °.
3. few teeth difference involute deceleration mechanism as described in claim 1, it is characterised in that: first planetary gear and eccentric shaft
Quantity be three or four.
4. few teeth difference involute deceleration mechanism as described in claim 1, it is characterised in that: the input terminal of the input shaft is one
A bevel gear wheel, bevel gear wheel are engaged with a bevel pinion, and bevel pinion is connect with external power mechanism.
5. few teeth difference involute deceleration mechanism as claimed in claim 4, it is characterised in that: the bevel pinion and input shaft
Bevel gear wheel engagement range is at 10 ° ~ 170 °.
6. few teeth difference involute deceleration mechanism as described in claim 1, it is characterised in that: the input shaft is close to input terminal
Gear is roller gear.
7. few teeth difference involute deceleration mechanism as described in claim 1, it is characterised in that: the input shaft passes through second few tooth
The centre bore of poor planetary gear, the aperture of the centre bore are greater than the diameter of axle of input shaft.
8. few teeth difference involute deceleration mechanism as described in claim 1, it is characterised in that: the eccentric shaft and the second few teeth difference
It is connected between planetary gear by needle bearing.
9. the few teeth difference involute deceleration mechanism as described in any one of claim 1-8, it is characterised in that: the first row
Carrier is equipped at least two reinforcers on the symmetrical position of central point, and reinforcer is located at the through-hole of the first planet carrier
Between；The identical reinforcer through hole of quantity is provided on the second fewer differential teeth planetary wheel, reinforcer can be inserted into reinforcer
In through hole.
10. few teeth difference involute deceleration mechanism as claimed in claim 9, it is characterised in that: offer axis on the reinforcer
The line pin hole parallel with input shaft axis, equally offers pin hole on second planet carrier, on reinforcer and the second planet carrier
Pin hole opposite penetrate through and by pin shaft connection.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821694446.9U CN209621972U (en) | 2018-10-18 | 2018-10-18 | Few teeth difference involute deceleration mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821694446.9U CN209621972U (en) | 2018-10-18 | 2018-10-18 | Few teeth difference involute deceleration mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN209621972U true CN209621972U (en) | 2019-11-12 |
Family
ID=68441142
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201821694446.9U Withdrawn - After Issue CN209621972U (en) | 2018-10-18 | 2018-10-18 | Few teeth difference involute deceleration mechanism |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN209621972U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109185398A (en) * | 2018-10-18 | 2019-01-11 | 陕西长空齿轮有限责任公司 | Few teeth difference involute deceleration mechanism |
-
2018
- 2018-10-18 CN CN201821694446.9U patent/CN209621972U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109185398A (en) * | 2018-10-18 | 2019-01-11 | 陕西长空齿轮有限责任公司 | Few teeth difference involute deceleration mechanism |
| CN109185398B (en) * | 2018-10-18 | 2023-12-29 | 陕西长空齿轮有限责任公司 | Involute speed reducing mechanism with small tooth difference |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20191112 Effective date of abandoning: 20231229 |
|
| AV01 | Patent right actively abandoned |
Granted publication date: 20191112 Effective date of abandoning: 20231229 |